Textile bobbin chuck



Aug. 19, 1969 D. M. MuLLlNs TEXTILE BOBBIN CHUCK 2 Sheets-Sheet 1 Filed Oct. l1, 1967 v INVENTOR. DAV/D M. MULLINS AGENT All@ 19,1969' D. M. MuLLlNs v3,462,092'

I TEXTILE BOBBIN CHUCK Filed ocr. 11, 195'/- A 2 sneetysheem I NVENTOR.

DAVID M. MULLINS www AGENT 3,462,092 TEXTILE BOBBIN CHUCK David M. Mullins, Pensacola, Fla., assignor to Monsanto I Company, St. Louis, Mo., a corporation of Delaware Filed Oct. 11, 1967, Ser. No. 674,613 Int. Cl. B65l1 75/30 U.s. cl. 24a-46.4 7 Claims ABSTRACT F THE DISCLOSURE A bobbin chuck having brake and clutch assemblies integrated to provide uninterrupted, sequential braking and clutching applications.

Background of the invention Surface or peripheral drive bobbin chucks are employed in textile processing for winding continuous yarns onto bobbins. Basically, such bobbin chucks comprise a sleeve, journaled for rotation about a spindle that is supported on a pivotal swing arm; a means` such 'as an expansible member for clutching or gripping a bobbin mounted over the sleeve; and, a braking assembly to retard and stop the rotation of the sleeve. The pivotal swing arm is employed to carry the bobbin chuck into and out of engagement with a drive roll and to accommodate for the growth in yarn package size during a winding operation. The term clutching refers to the holding or gripping of a bobbin on and the releasing of a bobbin from the bobbin chuck.

Surface drive bobbin chucks of conventional design have independently operable brake and clutch components and require several time and effort consuming steps to effect clutching and braking applications.

The bobbin chuck disclosed herein has clutch and brake components integrated to eiect sequential brake and clutch applications by a single manipulative step. The components are arranged to provide a uniform transfer of clutch and brake forces to a bobbin and to provide balanced rotational stability.

Summary of the invention The bobbin chuck has a pair of spaced annular members journaled rotatably about a hollow spindle. One of the annular members is also reciprocably or linearly displaceable on the spindle. Each annular member has a resilient ring mounted thereon for gripping or clutching a bobbin. A cylindrical sleeve is slidably supported on the annular members with the ends of the sleeve abutting against the resilient rings. A caged spring biases the linearly movable annular member in the direction of the other annular member to lock the cylindrical sleeve between the resilient rings and to apply sufficient force to cause the resilient rings to be compressed laterally and to expand radially outwardly. A bobbin mounted on the chuck, while the resilient rings are in a relaxed state, is clutched by the resilient rings when the latter are compressed.

The brake components comprise a pair of brake elementsone being carried by the reciprocable annular member and the other being connected to an actuating rod biased to maintain disengagement of the brake elements. A control means is operable for displacing the actuating rod in one direction to effect sequential braking and unclutching applications, and for permitting the actuating rod to return in the opposite direction to eiect sequential clutching and disengagement of the brake elements by respective bias forces.

Brief description of the drawing In the drawing: FIGURE l is a cross-section view of the improved bobbin chuck shown with a bobbin mounted thereon;

Patented Aug. 19, 1969 ICC Description of the preferred embodiment Referring to the drawing, FIGS. 1-4, the bobbin chuck consists of a hollow mandrel or spindle 2 supported at one end on a pivotal swing arm 4 and having oppositely disposed longitudinal slots 6 and an exteriorly threaded portion 8 at its opposite end thereof.

A pair of annular members, 10 and 12, are mounted coaxially and in spaced relation on spindle 2. Annular member 10 is rotatably journaled on a bearing 14, and annular member 12 is rotatably journaled on a bearing 16. Bearing 16 is mounted on a sleeve 18 supported on a linear bearing 20 in turn mounted on spindle 2, whereby annular member 12 is provided with rotary and linear displacement on spindle 2. Bearing sleeve 18, at one end thereof, has opposed slots 22 for a function to be described later. The bearings are retained conventionally, by shoulders provided on adjacent components and by retainer rings. Each member 10 and 12 has a resilient ring, 24 and 26, respectively, supported thereon with one outer lateral side of each ring, 24 and 26, abutting against a wall of its corresponding member 10 and 12.

A cylindrical sleeve 28 coaxially surrounds spindle 2, intermediate annular members 10 and 12, and is supported in slidable relation adjacent counterbored ends 30 and 32 on complementary annular shoulders 34 and 36, respectively, formed on members 10 and 12. Ends 30 and 32 abut against the inner lateral sides of resilient rings 24 and 26.

Annular member 12 is normally biased toward annular member 10 by the force of a coaxially arranged compressed helical spring 38 acting against a wall of annular member 12 at one end and against a retainer 40 at its opposite end. Retainer 40 is journaled on a bearing 42 mounted in a housing 44 threadingly coupled to the outer end of spindle 2 by coupling, shown between reference numerals 60 and 46 in FIG. 2, and which hereafter will be considered a part of housing 44.

Spring 38 has a value sufficient to displace member 12 in a leftward direction (FIG. l) whereby resilient ring 26, being in contact with end 32 of cylindrical sleeve 28, displaces sleeve 28 leftwardly so that the opposite end 30 of sleeve 28 applies a compressive force to resilient ring 24. Preferably, shoulder 36 comes in contact with the wall of the counterbored end 32 of sleeve 28 before spring 38 reaches its fully expanded value to compensate for a tendency of ring 26 to be compressed to a greater degree than ring 24.

Annular member 12 also has a coaxial annular brake lining or element 46 mounted interiorly therein. An annular brake lining or clement 48, complementary to brake element 46, is mounted on an annular backing plate 50'. Backing plate 50 has a transverse web 52 at the side opposite lining l48; and, web 52 has an internally threaded boss 54 joined centrally thereto. Backing plate 50 is mounted coaxially about the slotted end of spindle 2 with web 52 being slidably engaged within slots 6 permitting backing plate 50 to be axially displaced therein and to be constrained against rotation.

Brake element 48 is actuated by an actuating rod 56 that extends longitudinally through spindle 2 and is connected at one end threadingly to threaded boss 54 on web 50. At its opposite end actuating rod S6 has a cam follower surface 58. The slotted end of spindle 2 is closed ol by housing 44, and a helical spring 60 is positioned in the slotted end with one end abutting against the wall of housing 44 and the other end acting against web 52. Spring 60 is compressingly caged and biases actuating rod 56 leftwardly (FIG. 1) to a position where brake lining 48 is disengaged from brake lining 46 and the cam follower surface 58 engages a cam 62 formed at one end of a lever 64. Lever 64 is mounted pivotally about a pin 66 on swing arm 4, and has a handle portion 68 formed at the end opposite cam 62. A spring 70 (FIG. 3), mounted at one end on swing arm 4, acts at its opposite end against the handle 68 to bias lever 64 in a counterclockwise direction to a position Where the follower surface 58 of rod 56 engages the low side of cam 62 (FIG. 4). A retainer plate 72 guides and retains the cam end of lever 64.

For purposes of describing an operation, assume that the bobbin chuck has been swung or pivoted to a bobbin donning or mounting position away from a drive roll '74 (FIG. 3), that a bobbin 76 is to be mounted on the chuck, and that the bobbin chuck components are in the positions shown in FIG. 1. An operator applies a force to handle 68 of lever 64 to move the handle 68 downwardly against the force of spring 70, thus causing lever 64 to pivot in a clockwise direction (FIG. 3) whereby cam 62 displaces rod 56 rightwardly (FIG. 1) 4against the force of spring 60. Rightward displacement of rod 56 a predetermined distance carries brake element 48 into engagement with brake element 46 to effect braking of annular members and 12 and sleeve 28. Further displacement of rod 56 rightwardly, after engagement of the brake elements, against the forces of springs 60 and 38 will move annular member 12 axially to the right for carrying resilient ring 26 to the right, thereby removing the force being applied to sleeve 28 and resilient ring 24. The resilient rings 24 and 26 having the compressive force removed now relax and assume a normal configuration or state. The resilient rings 24 and 26 expand laterally and contract radially.

At this time, an operator dons or mounts an empty bobbin 76 on the bobbin chuck and slips the bobbin in position wherein the inner end of bobbin 76 contacts a flange 78 formed on annular member 10. If desired, a latch may be provided to hold handle 68 down while an operator mounts bobbin 76.

The operator now releases the force being applied to handle 68 so that lever 64 is pivoted by spring 70 in a counterclockwise direction carrying the high side of cam 62 away from the cam follower end 58 of rod 56. In sequence, spring 38 biases annular member 12 leftwardly (FIG. 1). The force applied by spring 38 will resilient member 26 on annular member 12 to compress and will cause shoulder 36 ou member 12 to act against a shoulder of counterbore end 32 of sleeve 28 to displace sleeve 28 leftwardly and cause end 30 of sleeve 28 to compress resilient ring 24. The force of spring 38 locks sleeve 28 between the resilient rings 24 and 26 and the latter expand radially outwardly into tight clutching contact with the bore of bobbin 76.

Upon complete release of force applied to handle 68, spring 70 returns lever 64 to its normal spring biased position as shown in FIG. 1 carrying the high side of cam 62 away from the cam follower end 58 of rod 56. Meanwhile, spring 60 biases rod 56 to its leftwardmost position, and rod 56 carries brake element 48 away and out of engagement of brake element 46.

At this time, bobbin 76, annular members 10 and 12, journaled spring 38 and sleeve 28 are free to rotate as -a coupled unit, and an operator can pivot swing arm '4 to bring bobbin 76 into engagement with drive roll 74 (FIG. 3) to begin a yarn winding operation.

Resilient rings 24 and 26 may be solid, substantially U-shaped, hollow or of any configuration providing uniform peripheral radial deformation.

It will be understood that variations and modifications of the bobbin chuck are expected to be covered within the purview of the invention.

I claim:

1. A bobbin chuck comprising,

a spindle supported at one end thereof,

a pair of spaced members mounted on said spindle,

one member being rotatably and the second member rotatably and reciprocably journaled thereon,

resilient means mounted on each of said pair of spaced members and being laterally supported at one side thereof,

sleeve means mounted about said spindle intermediate said resilient means and being slidably and reciprocably supported at its ends on said pair of spaced members, each end of said sleeve means contacting a respective opposite side of said resilient means,

bias means acting against said second member for biasing the same toward said first member to compress said resilient means between said pair of spaced member and said sleeve means,

first brake means mounted ou said second member,

second brake means mounted reciprocably and nonrotatably on said spindle and biased away from said first brake means,

control means for displacing said second brake means into engagement with said first brake means and for displacing said second member away from said first member, sequentially, and for permitting said second member to be biased toward said first member by said bias means for compressing said resilient means, and for permitting said biased second brake means to be carried away from said first 'brake means, sequentially.

2. A bobbin chuck as in claim 1, wherein said control means is operable in continuous sequence.

3. A bobbin chuck as in claim 1, wherein said resilient means are annular resilient rings.

4. A bobbin chuck as in claim 1, further comprising means for rotatably journaling said bias means.

5. A bobbin chuck as in claim 1,

wherein said spindle is hollow and is slotted at its opposite end, and

wherein said reciprocably and biasingly mounted second brake means has an actuating rod extending slidably through said hollow spindle, said actuating rod being actuable by said control means at one end thereof and having a biased brake assembly at its opposite end guided slidably within said slotted end of said hollow spindle.

6. A bobbin chuck comprising,

a spindle supported at one end thereof,

a first member journaled rotatably on said spindle,

a second member rotatably and reciprocably journaled on said spindle in spaced relation from said first member,

resilient means mounted peripherally about each of said first and second members, each resilient means being supported at one side thereof by its corresponding first and second member,

sleeve arranged concentrically about said spindle between said first and second members, said sleeve being slidably and reciprocably supported at its opposite ends on said latter members and contacting said resilient means at the opposite sides thereof,

first bias means for biasing said second member toward said first member for compressing said resilient means,

journal means at one end of said second member for rotatably journaling said first bias means,

first brake means mounted on said second member,

second reciprocable brake means guided slidably and axially on said spindle,

second bias means for biasing said second reciprocable brake means away from said first brake means,

control means for actuating said second reciprocable brake means into engagement with said first brake means, and said second member away from said first member to release the force applied 4to said resilient means, sequentially; and, for permitting said second member to be biasingly returned to apply a force to said resilient means, and for said second reciprocable brake means to be biasingly returned to a disengaged position, sequentially.

A bobbin chuck comprising,

hollow spindle supported at one end and having slot means at its opposite end thereof,

an actuating rod mounted slidably within said hollow spindle, said actuating rod having a cam follower at one end and a rst brake means at its opposite end guidably mounted within said spindle slot means, iirst member rotatably journaled on said hollow spindle,

second member rotatably and reciprocably journaled on said hollow spindle in spaced relation from said first member,

resilient ring mounted on said rst and second members, each resilient ring being buttressed at one side thereof by its corresponding iirst and second member,

a cylindrical sleeve arranged coaxially about said hollow spindle between said rst and second members, said cylindrical sleeve supported at its opposite ends on said latter members and 4contacting said resilient rings at their opposite sides thereof,

rst bias means for urging said second member toward said first member for compressing said resilient rings between said lirst and second members and said cylindrical sleeve,

journal means at one end of said iirst member for rotatably journaling said first bias means,

second brake means mounted on said second member and aligned with said iirst brake means,

a second bias means engaging said iirst brake means and normally biasing said first brake means to a position disengaged from said second brake means,

biased cam means engaging said cam follower on said said second member to be biased toward said iirst member for compressing said resilient rings, and to permit said iirst brake means to biasingly disengage from said second brake means, sequentially; in continuous sequence.

References Cited UNITED STATES PATENTS 2,042,968 6/ 1936 Siegenthaler 242-46.3 2,365,980 12/1944 Thomas 242-46.3 XR 2,564,746 8/1951 Bauer 242-46.6 2,733,874 2/ 1956 Petersen et al. 242-72 2,941,735 6/ 1960 Wyeth 242-46.2 3,052,420 9/ 1962 Roberts 242-46.3 3,092,342 6/ 1963 Jackson 242-46.2

U.S. Cl. X.R. 

